Vertical spindle milling machine



Oct. 18, 1949. F. A. HASSMAN ETAL 2,484,885

VERTICAL SPINDLE MILLING MACHINE Filed Feb; 25, 1944 7 Sheets-Sheet 1 ATTORNEY..

Get. 18, 1949. F. A. HASSMAN ET AL 2,484,885

VERTICAL snmm MILLING MACHINE Fil ed Feb. 25, 1944 7 Sheets-Sheet 2 TT LAL IN VEN TOR.

ATTORNEY.

Oct. 18, 1949. F. A. HASSMAN ET AL 4 2,484,835

VERTICAL SPINDLE MILLING MACHINE Filed Feb. 25, 1944 7 Sheets-Sheet 4 ATTORNEY.

Oct. 18, 1949. F. A. HASSMAN ET AL VERTICAL SPINDLE MILLING MACHINE 7 Sheets-Sheet 5 Filed Feb. 25 1944 A TTORNEY.

Oct. 18, 1949. F. A. HASSMAN ET AL 2,484,885

VERTICAL SPINDLE MILLING MACHINE Filed Feb. 25, 1944 7 Sheets-Sheet 6 117 26 9 l'z'q Z0 Iz'g 3 A TTORNE Y.

F. A. HASS MAN ETAL VERTICAL SPINDLE MILLING MACHINE Oct. 18, 1949.

7 Sheets-Sheet '7 Filed Feb. 25, 1944 Patented Oct. 18, 1949 UNITED STATES PATENT OFFICE VERTICAL SPINDLE MILLING MACHINE Ohio Application February 25, 1944, Serial No. 523,926

3 Claims.

This invention relates to transmission and control mechanism for machine tools, and more particularly for milling machines.

It is a general object of the present invention to provide improved control mechanism adapted for operation from one part of a machine to effect control of an apparatus in another relatively movable part of the machine.

It is also an object to provide a milling machine of the vertical spindle sliding head type with improved and simplified hydraulic compensating mechanism combined with hydraulic gear shifting apparatus operative to maintain constant relationship between hydraulic shifting apparatus in the column of the machine and hydraulically shiftable gearing in the sliding head for any position of the sliding head on said column.

And still another object is to provide an improved self-contained lubricating system in the sliding head of a vertical spindle Sliding head milling machine.

And a further object is to provide in conjunction with a fluid pressure speed charging system and a lubricating system located in the same chamber of a machine tool, an arrangement to isolate the fluid in one system from the fluid in the other system.

Other objects and advantages of the present invention should be readily apparent by reference to the following specification, considered in conjunction with the accompanying drawings forming a part thereof and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

Referring to the drawings in which similar reference characters are employed to denote the same or similar parts:

Figure 1 is a side elevation mostly in section of a vertical spindle sliding head milling machine on the line |--l of Figures 2, 3, 4 and '7.

Figure 2 is a fragmentary plan view of the milling machine particularly showing the top of the sliding head as indicated by the line 22 in Figure 1.

Figure 3 is a horizontal section through the milling machine on the line 33 of Figures 1, 4 and 7.

Figure 4 is a vertical section on the line 4-4 of Figures 1, 2, 3, 5, 8, and 9.

Figure 5 is a section on the line 55 of Figures 4 and 6.

Figure 6 is a fragmentary vertical section on the line 66 of Figure 5.

Figure 7 is a vertical section on the line 11 of Figures 1, 2, and 3.

Figure 8 is a horizontal section on the line 8-8 of Figures 4 and 9.

Figure 9 is a vertical section on the line 9-9 of Figures 2, 8, 10, 11, 12 and 13.

Figure 10 is a section on the line Ill-I0 of Figures 8 and 9.

Figure 11 is a section on the line I l-l I of Figures 8 and 9.

Figure 12 is a section on the line l2-I2 of Figures 8 and 9.

Figure 13 is a section on the line l3-l3 of Figures 8 and 9.

Figure 14 is a diagram of the circuit of the selfcontained lubricating system for the vertical spindle head.

Figure 15 is a diagram of the change speed transmission, showing the associated hydraulic control mechanism and lubricating system for the milling machine.

In some machine tools, particularly in a vertical spindle sliding head type milling machine having a change speed transmission for rotating the spindle at a selected series of speeds, it is desirable that the transmission apparatus be di vided into several independent speed changing mechanisms arranged in series relation and that one of the mechanisms of the series be carried by the sliding head carrying the cutter spindle. It is further desirable that a single remote speed changing control element, preferably mounted on the column or knee of the milling machine, be arranged to actuate all of the speed changing mechanisms in a predetermined sequence in order to establish any desired rate of speed for the spindle. As illustrative of such a milling machine to which this invention may be applied, there is shown a vertical spindle sliding head type machine, Figure 1, comprising a main frame or a column 28 having a knee 2| slidably mounted on appropriate guideways 22 formed on the front of the column. On the ways 24 of the knee is mounted the saddle 23, which in turn carries the work table 25 on appropriate dovetail guideways 26. On the upper portion of the column 2!! vertically slidable in guideways ill, Figures 2. 3, and '2, is the spindle carrier or head 28 in which is journaled the cutter spindle 29 against axial movement in appropriate bearings 30, 3| and 32 as best seen in Figure 7.

The sliding head 28 may be reciprocated vertically by any appropriate means such as an elevating screw 33, Figure 3, which may be fixed in the sliding head 28 and around which operates an elevating nut 34 journaled against axial movement in the column 20 and having formed thereon a bevel gear 35 which is engaged by a bevel gear 36 carried on a shaft 31 journaled in the column 20 of the machine and upon which a suitable actuating hand wheel (not shown) may be mounted for manual rotation of the shaft 31 or the shaft 31 may be actuated by any appropriate power means. In this way the head may be nicely adJusted up and down on the front of the column tomove thelcutter spindle 29 relative to the work table for effecting proper adjustment of a cutter on the spindle relative to a work piece on the table. In order to compensate for the natural downward pull of gravity on the-headiB- and thus facilitate its movement there is provided a counterweight 38, Figures 1 and 4, suspendedby suitable chains 39 passing over sprockets iifi journaled in the column I and connectedto'the top portion of the head 28 by appropriate chain anchoring studs 4|.

The main driving power for operating the milling machine cutter spindle and work feeding members is derived from the prime mover or main drive motor "'42-, Figure 1, appropriately mounted on a suitable'support 4-3 in thebase of the column 20. Themotor 'ez-has-adriving'pulley 44 from which power is transmitted'by appropriate belts 45' to-themain-drive clutch-pulley 46 carried on the pulley drive shaft 4'! journaled in appropriate'bearings 46in the column -26. The function of the clutch 46 is to connect or disconnect-the' driving power from the motor 4-2 with respect to the drive shaft 4'5, since the motor 42 is normally continuously --oper-ating when the machine is-in use. Any-conventionalapparatus, forming no specific part of this invention, may be utilized to control the'clutchpulley 46 for connecting or disconnecting power from the motor-"52 to the-shaft fl. Feed power takeoff for the knee, saddle, and table may be-obtained from the gear 49 which continuously driven by the motor 42 from the pulley lfithrough conventional apparatus whichforms no specific part of this invention and therefore will not be "described in detail herein.

The cutter spindle 29 is driven through a changespeedtransmission-in the column 20 and an associated change speed transmissionin the vertically-slidablehead 2.8: Both of these transmissions-are connected? in series and driven from the drive shaft l-l. Referringto the change speed transmission-inthe column 2-0, there is provided on the sha'ft 4"! aseriesaf shiftable gears 50 and 5|, comprisingagear couplet505l and a gear 52 axially :slidable in driving relationship on the sha'ft fil. Thegear'50 may bemoveddnto engagement with a gear--53; the.gear 5|: may be engaged with the 'gear 54, :and "the'l gear :52 engaged with a gearil55 carriedzonz a shaft 56. ljournaledsin. the column 21]: to thus eifect three changes of speed betweenitheshaft 41 and i-the =shaft56. On a shaft 5'! appropriately ijournaledinithe column 20 mountedaasliding gear coupletcomprising the-gears 58 and 59 which are respectively engageableiwithtthe gear "5.5z'and a gear 360 on shaft 56 to in this way provide two additional speed changesibetween' theshaft 56.-and.the shaft v51.

.The reversing gear-6i is mounted in sliding drivingrelationship onthe shaft 51 and may be moved into engagement with an idler gear 62 appropriately .journaled in thecolumn 20. The

idler gear BZalSohasanintegral. similar gear 63 connected in driving relationship with the gear 62. The latteragear '63 in turn isin cons'tantmesh with a gear 64 fixed on a shaft 65 journaledin the column 20. The reversing gear/6i may be shifted, as best seen in Figure .15, into engagement directly with the gear when movedto a position'6ia, thus driving the shaft. 65 in.one direction or the reversing gear 6l may be shifted into engagement with the gear "62 as shown to effect transmission of power from the shaft-51 through the gearing -6 l6'2- and" 63-64 to-rotate- ,the shaft 65 in the opposite direction to thereby provideja reverse to therdrivingtransmission and the" cutter spindle-2 9 associated therewith.

The reverse gear 6| may be shifted to either its position 6| or 6la by an appropriate reversing lever 66,-.Figure '15, carried in the column 61 and which actuates suitable linkage 68 and the shifter=fork--69 to effect the above movements of the --reversing gear 61 Fixedon the shaft 65 is a gear 10 and a gear H each respectively engageable by the gears 12 81111.,1l3: of. the shiftable gear couplet 12-13 slidingly mounted in driving relationship on a shaft! journaled in the. column 25. Also on the shaft 65 is journaled a gear 15 which may be connected "to or disconnected-'- from driving --engagement with -the shaft 65 by a clutch '16. Thegear 15 is constantly' inmesh with a gear 1-1 fixedon 'theshaft M; In 1 this way three speed changes may -be-obtained =between-:the shaft 565 and the-shaft bythe gear-engagements Ll--73,

NJ-=12, -and -by engagement *of the clutch 16 -so as to effect the drive' throughthe gears l51l; Onthe shaft 14 is fiXed-the 'driving g-ear- 18': which drives a gear 'l ll fixed on-the shaft- 28 0' appropriate- 1y journaled in bearings 8 land- 82 in the column 26. 0n=theouter end'of the sh aft 8ll is formed a beve1 pinio1'1' 83, --Fi'gures 3 and"4',=which drives a bevel gear. "84 'fixed to a--=sleeve 8'5' 'journa1ed i'n appropriate;bearings- 86 'and 8 in the-column 26 of the machine. The above-described gearing mechanismxcomprises the change-speedtransmissionainithe column Zfl ofthe millihgmachine.

Power from 1 this change speed" transmission in the column-is transmitte'd' tdthe vertically movable spindle 29 with head 28 through therdrive shaft :88; Figures'3 and 4,-which has:a'downwardly extending portion having splines -89 formed thereonwhich slidingly fit' in; driving engagement insthe spline'd'bore?!) 0 of the sleeve Y 85. The shaft 68' is 'journaled 'againstuaxial movement in the spindle head 28 on appropriate bearingsfil and 92. Theshaft 8'8Z-t-hus=may be driven at all times for any :vertical position:of the :spin'dla-head' 28 onlt'he column ffl:

-'A -.changerspeed transmission is provided between thisv-shaft' 88 -andthe cutter spindle 29 comprising al-high speedfdriving gear-"93 journaled for. free rotation on suitable-bearings 94 on the shaft-88 asi-best seeninlFigure' ls; Also'slidably mounted in-driving engagementon splines- -95 formed on the shaft 88 is shiftable member QG, Figures 4, 5 and 6. The-memberilfi has a low speed drivinggeanor backgear pinion 91-which may engage the large low speed driving gear 98 fixed on the :cutter spindl'e' 29 when the member 96 "is in :a lower :downwardly shifted position,

Figures 1 and 4 When the m'ember 96-is shifted upwardly to theihiglh: speed 'position its internal clutch: teeth "9 9 engage: mating clutch teeth l 00 of. the'lhigh speed:drivingiagean flti so as to-positively lock the gear 93 in driving relationship with the-:shafttfi88 while rat i the same time disengaging i-the @gea-r 57:5 rfromz-l'the gear 98- on "the cutter spindle.

change speed transmission in the slicling' spindle In this" head 28. It is to be noted that the change speed transmission in the column 20 and the change speed transmission in the head 28 are connected in series through the shaft 80 and associated gearing so that by shifting the gear members in both of said transmissions in appropriate sequential relationship the entire range of spindle speeds may be obtained for the cutter spindle 29.

In order to effect this sequential operation of the change speed transmissions it is desirable to effect all of the changes from a single remote control point comprising single lever control preferably located on the column 20 or at a convenient location on the knee 2| of the machine. The problem, however, is complicated by the fact that a portion of the change speed transmission in the spindle head 28 has bodily relative movement with respect to the change speed transmission mounted in the column. It is, therefore, necessary to provide a mechanism effective at all times to shift the member 06, Figure 4, of the change speed transmission in the head 28 in proper sequential relationship with the change speed transmission in the column for any relative vertical position of the head 28 on the column 20.

In order to obtain these desired results a hydraulic gear shifting control system, as best illustrated in Figure 15, is utilized comprising a main control valve I02 which may be supplied with fluid pressure from a reservoir I03 formed in the base I control valve I02 may be rotated or driven, pref-' erably by power, to a series of predetermined positions for selectively applying fluid pressure from the line I06 to hydraulic actuating means for shifting the various gears of the change speed transmission in the column 20 and spindle head 28 in a predetermined sequence to effect the entire range of speed changes for the cutter spindle 29. The use of such a selector control valve for hydraulic gear shifting is generally set forth in Patent No. 2,012,081, issued August 20, 1935, and therefore further detailed description of the specific structure of the control valve I02 will not be undertaken.

The valve I02, referring to Figure 15, may be driven from any suitable means such as a power take-off gear I I connected to the pulley 46 which drives a gear III of a shaft II2 which, through appropriate spiral gearing indicated at I I3, drives a bevel gear I I4 which engages a pair of reversing bevel gears H5 and H6. These reversing bevel gears may be engaged alternately to a drive shaft II1 by shifting the reversing clutch IIB through the linkage II9 connected to a control lever I20 which may be conveniently located on the column 20 or the knee 2I as desired, said control lever I20 serving to select the entire range of speeds for the cutter spindle 29. When the lever I20 is shifted to actuate the reversing clutch IIO power may be transmitted in one direction or the other through the gears I2 I, and I22 and the gear fixed to the operating shaft I24 for the control valve I02. An appropriate dial indicating means, indicated generally at I25, may be provided to show the relative position of the valve I02 and therefore the speed selected for the transmission.

A suitable relief valve I01 connected Fluid pressure from the line I06 is selectively distributed by means of the valve I02 through the lines I26 and I21 to the actuating cylinders I28 and I29 for the shifter fork I30 to shift the gear 52. Fluid from the valve I02 also is distributed through lines I3I and I32 to the respective operating cylinders I33 and I34' for the shifter fork I35 to appropriately actuate the gear couplet 5I to its selectable positions. 58-59 is actuated by the shifter fork-I 36 operated by the cylinders I31 and I38 connected to the control valve I02 by the lines I39 and I40. The clutch 16 on the shaft 65 is actuated by a shifter fork MI by the cylinders I42 and I43 connected to the valve I02 by appropriate lines I44 and I45. Similarly, the gear couplet 1213 is actuated by the shifter fork I46 by cylinders I41 and I48 connected by lines I49 and I50 to the selector valve I02. The detail structure of the various cylinders for actuating the shifter forks I30, I35, I36, MI, and I46 are of conventional construction as shown in the above-mentioned Patent 2,012,081, and therefore will not be described or shown in detail herein, it being sufficient to State that rotation of the valve I02 to its selected positions will apply pressure and permit exhaust from the respective operating cylinders for the shifter forks to provide a complete sequential operation for the associated shiftable gears in the column 20, exhaust from the cylinders being discharged through the valve I02 and the exhaust or drain line I5I for return of the fluid to the reservoir The change speedtransmission in the sliding spindle head 28 is also shifted in sequential relationship with the shifting of the gears in the lines I52 and I53 which communicate with hydraulic shifting mechanism and compensating mechanism for the member 96 on the shaft 88. Referring particularly to Figures 3 and 4, the line I52 is connected to drilled passageways I52a, I52b, I520, I52d, and I52e, which connects with an annular groove I54 which groove communicates through ports I55 formed in the bottom .portion of the shifting and compensating cylinder I56. These ports I55 open into passageways I51 which communicate with grooves I58 formed in the outer surface of the cylinder I56 and which are closed by means of a sleeve I59 closely fitting over the outside of the cylinder I56. The grooves I58 communicate in turn with a passageway I60 connected to a port I6I which opens into the inner chamber I62 in the cylinder I56 above the piston I63 which is connected to the piston rod I64. The line I53 is connected through passageways I56a, I531), I530, I53d, I53e, and I53 opening into a chamber I65 which communicates with the lower chamber formed in the cylinder I56 below the piston I63. Thus, fluid pressure may be applied in one or the other of the lines I52 and I53 to reciprocate the piston I63 upwardly or downwardly in the cylinder I56.

Referring to Figures 4, 5, and 6, the piston rod I64 extends upwardly through a supporting gland I66, carried by the cylinder I56 and has a reduced end portion I64a which passes through a clearance bore I61 mounted in a cross pin I68. The cross pin I68 is confined against axial movement relative to the piston rod I64 but is permitted free rotation thereabout by means of a pair of thrust bearings I60 and I10 located each side Of the pin I68 and confined on the piston rod I64 by an ap- The gear couplet,

ease-seas propriate= adjusting emit :I 12.5 Alilubrieant shield I I If is also fixed bnthe pistontrodcl 6t ibelowithee thrust: bearing I 69.5 The crossr-pim I 68; ireferring 1 more iparticularly to- Figuresafiliandutig isiaxiallyr reciprocabl'e' in a diametralfsl'ot il 13 :formedinrthe 5 shaft 883- There is also :providedianiaxialiboresl M' i formeddn the shaft tii to accommodateithe nut: i

I 12,ithe:thrustbearings! 69-:and :I I9 fonttheupper endsofs the.-.piston.rod,.andthe lubricant shield -:I I I reciprocable axially inside the shaft 88:1The cross.

Thus; when fluid pressure is applied zthroug'hix theline'I 52 'and' conveyed tdthe upperschamben:

I 62 3a=bovethe piston" I 63 m the cylinder I 56- 'to urge the piston downward; the gear 1 97: of: Fishes; member "9 6 will be: brought into engagement with :v the low speed-gear at to efiectlowspeed'drivingpf: Q 5 the cutter =spindle 29 Wh'enth'e fluid pressure applied through the line I 53 below the-pistonzl 63 I to fo'rc'eit upwardly in the 'eylirider l 56 themem-L- ber- 96will b'e-moved upWa'rdly'to-engage its clutch?- 99-"with' the clutch I 09 bf'the-high speedgear 93 1; 1 efiect high speed drivi-ng-nft the cutter spindle-29 through the "gears 93-'-I-9I-. A series otfloal'anced': spring-urged ball detents, Figure 5, indicated at;

I 18; operate in de'tentinotcheszsl 'I9 formed-simth'e splines 9 5 of the shaft 89 serving to lnorma'lly \hold 113.; the-member :9 6 in its. upper. shifted position: intrthe -1. event fluidpressure should be cutioirzfrom therlinec I 53-when 'itis desired to maintaimthe hig'h'zspeed-i driving-positionfonthe membrzBBi- It is-to be'further notedthat'ithisi hydraulically t o actuated shifting mechanismier thesmemberi96'5 of 'thespindle head change 'speed itransrnission 1 also funotions anal automatic 2 compensating device whereby the gear 96= may i beflmaintained in" either its -upper or lowershiftedopositions; as 4; determined by" the setting ofthee controh valve =2 I02 Figure lilj in the column',-at all tirhes fdrwany' positionof the head" '28 fon iits guide'wa'ysfl ZIl'on 1' whether it isbeing fed up: or idown' b'y meansfof the actuating screw 33 an'd assoeiate'd mechanisms .50 The cylinder 4 I 56 made relatively long; permit-z ting a greater 2 amount of relative travelliof :the piston I 63 in'th'e'cylinder: I 56ithanl;iswreq-uiredto: shift'the gear member 96 the *diStancerdnditatezd: by the arrow: IIQ' inL FIgure' 4. This additional-.55 movement of a the piston= '-I 63 m the cylinder :I 5 6 is: provided to take' care' -of the relative :movernentrt of the spindleshea-d-n :on the columniwhil'e :maint-i taining the gear member 96 in either: of itsshif ted i positions by fluid pressure' from the control valvecoo I92 and=pump I04:

Whenthe member 96 is-shifted in it's downwardra or low speed position, as shown: particularly in: Figures 1; 4, and-d5,"- fiuid'lpressure 'zwi-ll :come Linn through the line I52 and into the *ch'ambenrIGZi; 65 above the piston I 63- to hold the icrossr pin '1 I 68 down against'ithe arcuate bottom portion .IIKdi ofthe slot I I3 and thereby-hold the ;tgear:mem'-; ber 96 'fixed with respect tootheeshaft 682m itss lower position wi-th it's gear:9'I' in running ensgagement' with the gear 98 oni the cutter spindle 29: The'ch'amber on=the=lower'side iof the pistonn I63 "at *this time is conneetedthrou'gh the line 1 I53; control valve- I 02, with the drain =lih'e I 5? to -the reservoir I 033 Should-*the spindlemead- 2fl iundertrtheseeconditions be raised: fluidrpress sure inthe chamber I62 would be displaced thereftormas apistonrod I64 and piston: I63 is moved upiby'the:upwardzmovement of the head 28, this displaced fluid escaping back through the control valve'wIMiagainst the pumppressure from the 7 pump IM-iand out through the relief valve I01 to the reservoir. I03,tthus maintaining the pressuresholdingthe gear member 96 downward while system}; As the piston. :.I 63 is thus moved upward fluidiwillibei drawn in through the line I53 through the :valve IBZand through the exhaust line I5I from the tank I 93 so as to maintain this zsidezofthe rcylindernI56 properly supplied with fluid;

Similarly, should the head be moved downwardly underthese conditions, fluid pressure from thepumpvIM passing through the line I96,-con trol valve I 62 (and the line I52 would keep the upper chamber I62 abovevthepiston I63 'continuously=filled with fluid pressure to cause the piston. I63 .to move downward with the downward I movement "of the spindle head. 28, thus always keeping. thev gear 96 in its downward shifted I position. Fluid will, of course, be displaced from the .chamberzbelow the piston I63 in the cylinder .156 out through. the line I53, the control valve pressureirom' thezcontrol valve I92 through the line1l53that the gear member 96 will be moved tion OfipIGSSUTQ throughthe line I53 will likewise keep the gear 96 in'its upper engagedposition 961 with the gear 93 1 for any upward 'or downward;

motion of the spindle'carrying head 28.-

In this way is provided a combined hydraulic gear. shiftingrm'echanism and compensatingdevice for; maintaining a shiftable member of a' movable change speedtransmission in any desired:predeterminedshifted position, irrespective of the relative position of movement of the movable transmission with respect to a remote control m'eansfor effecting the shifting. It will also be noted that 1 there is provided a fluid pressure shiftable; change speed'i transmission, part of which is: mounted .in one member 2 and another part of.which is -mounted vin another linember movablezrelative to said first-mentioned member -in:':which;the entire change speed transmission may. be operated in .a complete sequential seriesof 'speedtchanges for-any relative movement or positionxof themovable member with respect to thel-other member 'of'the change speed transmission:

Associated withrxthe sliding; spindle head 28 andvcooperating withtheidrivingmeans for the cutter .spindlerincorporating:the hydraulic shifting,mechanismiand 'motion.compensator, is a selfcontained lubric'atihgsystemior the spindle head mechanism.. In this arrangement the shaft 88: isiutilizedas. az-drive shaft for rotating the cutter spindle and'for' actuating a lubricating transmission system incorporated in the'sliding head 28' s'and deriving its source of lubricating fluid from displacing the fluidhfromthe pressure side of the wholly within said spindle head 28. On the upper end of the common drive shaft 88 are mounted a pair of vane pumps having rotors I88 and HM respectively as best seen in Figures 4 and 14, each of which is keyed to the reduced end portion 88a of the shaft 88 by keys I82 and I83. In slots I84 of the rotors are mounted vanes I85 which are urged radially outward by springs I85a.

Referring to Figure 1&4, when the shaft 88 is rotating the rotor I88 clockwise, pressure will develop in the arcuate portion I86a while suction will develop in the arcuate portion I868 of the eccentric bore I860. Under these conditions, the port I88 is a pressure or delivery port while the port I81 functions as a suction or intake port. Fluid pressure is thus transmitted from the port I86 through a line I88, line I89, and check valve I98 into the main lubricating supply line I9I. The check valve I92 under these conditions remains closed so that there will be no flow through the line I93. Similarly, intake of fluid to port I81 comes through suction line I94, check valve I95, and lines I96 and I91, the check valve I98 being closed under these conditions.

Upon opposite rotation of the shaft 88, as when the reversing control lever 68 is operated, Figure 15, to reverse the spindle drive transmission for opposite rotation of the cutter spindle 29, the port I86 becomes an intake port and the port I81 becomes a pressure port. Under these conditions fluid will be drawn in through the line 288, check valve I92, line I93, and line I88 to the intake port I86 during which time the check valve I88 remains closed. Delivery fluid will be transmitted from the port I81 through lines I91 and I9 9, the check valve I 98 into the delivery line 28I, the check valve I85 remaining closed under these conditions. The lines I94 and 288 which are normal intake lines for the pump for either direction of rotation of the shaft 88 are connected to a common suction line 282, while the lines I9I and 28! are connected together for delivery of lubricating fluid to a pair of supply lines 228 and 22!.

Similarly, the pump I8l has ports 285 and 288 each of which may alternately supply pressure or act as intake ports depending upon the direction of rotation of the shaft 88. Thus, the pump I8I normally may withdraw fluid through the strainer 281a of a main suction line 281 through lines 288 and 289 and deliver it under pressure to a main supply line 2I8 through lines 2 and 2I2, check valves 2I3, 2I4, 2I5, and 2I6 as explained in the case of the pump I88.

Preferably the entire arrangement of pump discs, vanes, check valves and circuit shown in Figures 8, 9, 10, 11, 12, 13 and 14 is incorporated in the main pump head 2I1 which is mounted on top of the spindle carrier or head by appropriate screws 2I8 so that the reduced end portion 88a of the shaft 88 properly carries the discs I88 and I8I of the pumps in proper relationship to the eccentric bores I860. In this way, the entire pump assembly is mounted on the spindle head 28 at the top of the common drive shaft 88 and the Various intake and discharge passageways enter and leave the pumps through appropriate openings formed in the member 2I1.

In this self -contained lubricating system for the spindle head 28 there is thus provided two separate fluid pressure pumps I 88 and I8I driven by the common drive shaft 88, the pump I88 serving to effect the general lubricating of the change speed gearing and associated bearings and the upper portions of the spindle bearing mounting ill in the head. The second pump serves to provide means for lubricating additional parts of the transmission but more specifically for lubricating the lower spindle bearings and for removing surplus lubrioant which may accumulate around the lower spindle nose portion of the head where the spindle projects outwardly through the bottom of the head. Thus, the latter pump serves to prevent excessive lubricant, utilize for lubricating the spindle bearings, from escaping out of the spindle head and on to the cutter and work and to thereby serve to prevent loss of lubricant from the head 28.

The pump I88 delivers fluid pressure through the line 283, Figures 9 and 15, into a passageway 2I9 from which the flow divides, part of it passing out through an opening 228 where it sprays upon the bearings 9| and 94 of the drive shaft 88 and the high speed gear 93 respectively and is ultimately caught by the reservoir 231, Figures 4 and 15. The other part of the flow from the passageway 2 I9 passes out through the opening 22I to discharge on the upper spindle bearing 32 and downwardly therefrom on the gear I8I and gear 98. Fluid is delivered from the pump I8I out through the main supply line 2I8 through a passageway 222, Figure 9, and out through an opening 223 from which it discharges on the shiftable member 96, the thrust bearings I89 and I18, and the lower supporting bearing 92 for the shaft 88.

There are two separate fluid catchment reservoirs provided in the spindle head 28 to receive the fluid discharge from these pumps I88 and I8I. The major lubricating flow circulated by the pump I88 out through the line 22!, Figures 9 and 15, is caught by the reservoir 224 formed as a cavity in the spindle head 28. Normally, the reservoir 224 is kept filled with liquid up to a levelshaft 88 is not rotating), from the passageway 224a forming part of the reservoir 224 through the line and associated passageways 282 returning to the intake lines I94 or 288 of the pump I88. Thus the pump I88 circulates fluid through the line 22I which is ultimately received in the reservoir 224 after supplying and lubricating the various mechanisms associated with the spindle 29 and is withdrawn therefrom by the pump for continuous recirculation, the reservoir 224 maintaining a substantially continuous level of lubricant 225 during this operation.

Fluid delivered by the pump I8l through the line 222 and opening 223 passes in part through the bores I13 and I14 in the shaft 88, Figure 4, past the lubricant shield I1I into a chamber 221a formed by a threaded sleeve 228 mounted in the bore and having an upwardy extending cylindrical sleeve portion 228a projecting inside of the lubricant shield member I 1 I. Lubricant accumulating in the chamber 221a will overflow out through a passageway 229 formed in the shaft 88 and escape outwardly and down through the bearing 92. It will be noted, however, that fluid from the chamber 221 cannot rise above the portion 22811 of the sleeve 228 since it is above the drain opening 228. Similarly, no fluid escaping through the bore 238 in the gland I66 can get into the drain opening 229. Therefore, the hydraulic actuating fluid for the gear shifting mechanism cannot mix with the fluid in the lubricating system in the head 28 since any fluid that may escapearound the-piston rod 164 at the bore 230passes down through: the clearance space 231. formed'iby theenlarged bore 232m the shaft 88 surrounding the sleeve member 459 of the cylinder l56 from where'it drains out the bottom of the shaft88-in'to the-columncompartment containing themain supporting bearings 86 and 8! for the sleeve 85 from where it is returned to the reservoir 103 in the column- 20. Thus, in this way, fluid for the actuati'ng'system of the gear shifting mechanism is: kept separate and independent of the lubricating fluid for the self-contained lubricating system in the spindle head 28.

Fluid passing down through the bearing 92 drains over the lubricant shield 233, Figure 4, and then out through a passageway 234, Figures 1 and 15, over the spindle bearing 3| and downwardly through the opening 235, Figure 7, to lubricate the lower spindle bearing 30. Lubricant accumulating in the chamber 235 below the bearing 30 is drained off through a passageway'236a into a reservoir 23'! formed in the spindle head 28 around the lower portion of the spindle nose 29a and of the spindle 29. The pump-I8 I continuously withdraws fluid through the check valve 201a (which maintains the line 20'! charged with fluid when S3 is not rotating) the line and associated passageways 20! so as to prevent any accumulation of fluid in this reservoir 23] and the chamber 236 to-thereby prevent fluid from flowing around the lubricant shield 238 at the lower end of thespindle 29 and thus escaping out through the space 239 around the spindle 29 and dripping upon the cutter and a work piece on the work table 25 which would result in' interference with the proper manipulation of the machine and loss of lubricant from the spindle head 28;

In this way an eflicient self contained lubricating system has been provided for a vertical spindle sliding head for a milling machine which continuously recirculates lubricant throughout the head mechanisms without loss of. fluid therefrom and without intermixing the lubricating fluid with other fluid circulating systems of the machine. It is to be further noted that this selfcontained lubricating system for the vertical spindle sliding head is actuated from a common drive shaft which also-rotates the cutter spindle at a plurality of different speeds, said shaft containin means for effecting said diiferent speeds and having compensating mechanism whereby said speed changes may beobtained for any relative position to which said'head may be moved.

What isclaimed is:

1. In a machine tool, a frame, a spindle carrier movable on said frame, means for'driving a spindle journaled in said carrier at a plurality of dif ferent rates of speed comprising a change speed transmission in said frame, a change speed transmission in said spindle carrier serially connected with said change speed transmission in said frame. a prime mover in said frame connected to drive said change speed transmission in the frame, means for moving said spindle carrier on said frame, and hydraulic actuating means for effecting speed changes in both of said change speed transmissions in sequential relationship to effect a complete range of speed changes in said spindle for any positionv of said spindle carrier on said frame, including a piston andcylind'er, one of which is attached to the frame: and the other connected toa shiftable element inthe carrier.

2; In a vertical spindle sliding head milling machine, a column, a spindle headverti'callyreciprocable on said column, a cutterspindle journaled in saidhead, a shaft journaled in said head, a change speed transmission interconnecting said shaft and said spindle, a primemover in said column, means in said column engaging said shaft by sliding splined driving connection. permitting rotation of said shaft by said prime mover for any relative-position of; sliding movement of said head on said column, a shiftable gear member on said shaft movable axially thereof to' effect speed changes in: said change speed transmission, afluid pressure actuatingv cylinder'mounted on said: column and telescopically. positioned in saidshaft; a piston havin apistonrod operating in said cylinder, said piston rod'being connected tosaid shiftable gear member, a source of fluid pressureinsaid column, anda control devicefor saidsource of fluid pressure for alternately; connecting said pressure. to one'endor the other of said cylinder for recipro eating saidpiston' rod to effect shifting of said shiftable gear member, said cyinder" serving to shift said gear member and to automatically compensate for the movement ofsaid head-Von said column while maintaining said gear member in desired predetermined shifted: positions;

3. In' a milling machine having a-spindle carrier, a column. for supporting; said' carrier for relative movement thereon; a. cutter' spindle journaled in said carrier, a" prime mover'mountedl in the column, a' change. speed transmissioniforcone necting the prime mover to the spindle including aiirst part of. said transmissionrmountedl'in said column and a'second part of said transmission being mounted in the carrier, each of said parts includingzshiftable elements for varying the speed of said spindle; a" fluid pressure control mechanism for governing; the shifting of said parts in both of said transmissions in-a" predetermined sequential relationship to produce a prescribed range of speeds for said spindle, fluid operable means for shifting the elements of the second part of" said transmissionincluding av piston and cylinder havingi'its axis paralleltothe-movement of said carrienone of said-partsbeingrfixed and the other connectible to' the shiftable element, and means in said mechanismtfor connecting 'a' source of fluid pressure selectively to one end or the other of said cylinder andimaintaining'said pressure to holdthe shiftable element in either one of its shifted positions during movement of the carrier.

FRED A. HASSMAN. CHARLES. HERFURTH'.

REFERENCES; CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 974,392 Junggren Nov. 1, 1-910 1,561,076- I-I'eitman Nov. 10, 1925 1,653,576 Klausmeyer Dec. 20, 1927 1,832,487 Kearney et'al Nov. 17, 1931 2,129,307 Moo Sept. 6, 1938 2,242,445 Armitage May 20, 1941 2,349,597- Nenninger et a1 May 23,1944 

